DE2640752A1 - ROTARY VIBRATION DAMPER - Google Patents

Description

Applicant: Dr. Dirk Forkel, Eichenweg 18, 8520 E

Ä5Ä & 752

Torsional vibration damper

The invention relates to a viscous Friction means working torsional vibration damper to limit the vibration deflections and thus the Stress especially on crankshafts in internal combustion engines. Such vibration dampers are known in different versions and basically consist of a fixed with the Flange body connected to the shaft and a flywheel attached to it rotatably or elastically, which, together with corresponding surfaces of the flange body, forms narrow gaps which are filled with a highly viscous liquid. In the case of Torsional vibrations occurring between the flange body and the flywheel acting as an inertial mass Relative movements result in strong shear forces in the gaps and thus the desired damping effect.

Depending on the arrangement of the flywheel, you can choose between dampers with an internal flywheel, in which the flange body is designed as a housing and fully encloses the flywheel, and such with an external flywheel, where there is a gap between the flange body and the gap comprehensive flywheel seals are required.

Although the last-mentioned embodiment with external flywheel would have obvious advantages in the greatly reduced fixed

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Mass of the flange body based on the omission of the housing and the accessibility of the flywheel are, in practice so far only the closed version with their simple structure enforced. However, this version has a number of weaknesses make them more and more unpleasant, especially in engines that are subject to higher loads.

A particular disadvantage is the limitation of the gap area, soft through the surface of the rotating ring is given, and as a result, very narrow gaps that are inevitable to achieve optimum coupling with the available oil viscosities, and as a further result, the very low volume of viscous friction means in which the entire work of the damper has to be converted into heat.

It is well known that between the three sizes mentioned for a given viscosity and a given diameter, that the coupling of the gap area is proportional and the gap width is inversely proportional, while the volume corresponds to the product of both sizes. For example, it would double allow twice the gap width and four times the gap area compared to conventional dampers Work volume.

The disadvantages mentioned are therefore all related to one another and not only require high surface quality and dimensional accuracy , but also easily lead to thermal and mechanical overloading of the silicone oils used and thus to the uselessness of the damper.

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In addition, the internal pressure that occurs during operation as a result of the increase in temperature undesirably deforms the housing, which results in a decrease in the damping effect and can also cause the flywheel to tarnish and seize on the housing. Another problem is the very precise guidance of the flywheel with the help of the usual sliding bearing , which is particularly important at higher loads and when axial vibrations occur due to the poor lubricating properties of the silicone oils used and the relatively narrow bearing clearance in which they are stressed beyond their shear strength can, is at risk.

The fact that so far no practically usable solution for a viscous damper with an external flywheel has been found, is apparently due to the fact that here not only the disadvantages of the closed design are avoided, but also additional problems that arise from the additionally required seal between the flange body and the flywheel, as well as further solid sealing surfaces between the individual parts of both bodies in view of the significant creep ability (low surface tension) of the silicone oils used and the internal pressures that occur. In addition, there is the task, which is very important for practical implementation, of finding a design for this basically more complex damper design consisting of more parts, which enables a competitively cheap production with non-enlarged external dimensions.

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Solution proposals have become known, in which, instead of sliding seals that are unusable in continuous operation, elastic seals are used Material suggested below Pretension are or are vulcanized and at the same time the genpue guidance of the flywheel should take over. Such a design (for example in the German Auslegeschrift 1295287), however, has the Disadvantage that with sufficient radial and axial rigidity the necessary movement in tangential direction when torsional vibrations occur only by sliding or by strong Deformation is made possible, both of which lead to destruction would result in continuous operation. Even with another proposal after the German one Open! Ed. 2302128 addresses this problem not solved because in the case of vulcanized rubber rings - because of the small amount available placing place to a greater extent - the same applies, while with the also proposed The durability of the O-rings cannot be achieved with plain bearings. Summarized therefore have the proposed solutions for combined storage and sealing that have become known of the flywheel compared to the flange body has the disadvantage that it meets the requirements great accuracy and consequently rigidity in the radial and in the axial direction at the same time sufficiently large elasticity in the circumferential direction can not be sufficient, and that they also not have the volume to be able to absorb the deformation work that occurs in continuous operation.

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In addition, no precautions are taken to prevent damage to the seals themselves To prevent an increase in the internal pressure when the damper heats up, or the seals accordingly to protect.

Regarding the tight seal between the individual parts of the damper to be assembled an execution according to the German Auslegeschrift 1295287 appears without any problems, in this one In this case, however, the gap area is no larger than with conventional closed damper designs. In contrast, the arrangement shown in German Offenlegungsschrift 2362128 allows a certain enlargement of several interlocking disks and intermediate rings of the entire gap area (which, however, is due to the given external dimensions of the damper the division into a mass part and a damper part provided here can hardly be exploited), but it buys that with the disadvantage of four flat seals per pair of lamellae or correspondingly precisely machined sealing surfaces, which in 1instead requires higher manufacturing costs.

The object of the invention is therefore to address both the aforementioned disadvantages of conventional viscosity dampers with internal flywheel as well as those of the previously known design proposals to avoid for dampers with an external flywheel.

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This task is performed with a torsional vibration damper with internal flange body and external flywheel, the several interlocking Have damper washers, their gaps filled with highly viscous liquid and sealed with elastic material are, according to the invention achieved in that the flange body and / or the flywheel as Damper washers lamellas bears on the fastening edge topfarti «; to achieve greater Stiffness and better heat conduction are cranked according to the desired distance, and which are made relatively so thin that their thickness is at most five times the gap width, preferably even twice the Gap width is. With a sufficient number of such thin slats, preferably can be punched and pressed from Dlech without increasing the dimensions of the damper the decisive enlargement of the cleavage areas in a very economical way at strong achieve reduced accuracy requirements.

In one embodiment that is particularly suitable for large dampers with relatively high lamellae with a correspondingly large outer diameter, these lamellas are paired with different bends that they have precisely defined distances outside when assembling, and that they have a disk-like inside Extension are kept close together and form part of the mounting flange.

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The outward in the axial direction and on the the strongest warped lamellas contribute to this Your cylindrical or conical part expediently the combined elastic bearings - and sealing rings, which are thus fastened on the one hand to the flange body and on the other Page in an overlapping sheet metal cap of the Flywheel and support it with it.

In another embodiment, the mentioned sheet metal caps can be on the front side of the flywheel be pulled up and enclose this on the outer diameter with a cylindrical edge. This takes place the attachment of the sheet metal caps to the flywheel in the vicinity of the outer diameter, with a simplification of the Production and sealing results when the two sheet metal caps in the vicinity .der the center plane of the The flywheel almost collide and only a single seal or weld seam is required do. The sheet metal caps can advantageously be dimensioned and membrane-like, in particular at their end faces be designed so that it changes in volume of the damping fluid due to temperature on the inner diameter in the axial direction (due to the given elasticity of the bearing) can evade something, which keeps the pressure increase inside the damper low.

In another version, the wide, elastic bearing and sealing rings are not included. her . Outside diameter, but with the inside diameter

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on a correspondingly designed part of the flange body. In this case they carry the flywheel on corresponding surfaces directly without the use of overlapping caps, whereby the front-side disks of the flywheel at their inner diameter for support on the Bearing ring can be widened. In this embodiment, the volume compensation is expedient made possible by an annular sheet metal membrane attached to the front of the flywheel, which is e.g. welded with two ring seams and with the interior of the damper through a Bore is in communication.

In another embodiment, which is particularly The lamellae are suitable for smaller and larger quantities of dampers in an annular space, the outer diameter of the flywheel and the inner diameter of the Flange body is limited, and are alternately attached to the flywheel and the flange body, where both groups of lamellas are equal to one another. The bend on the fastening edge serves not only as a spacer to the next slat and for stiffening, but also for better fastening of the slats. For manufacturing reasons, the individual slats can also be made in two parts, with the two parts, e.g. the cylindrical and the flat part, for example soldered together are. The group of those attached to the flywheel Lamellae (outer lamellae) can also consist of thicker lamellae and ring-shaped spacers be composed.

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In the Damnfer version with the same in groups For economic reasons, lamellae will have a limited selection of diameter pairings limit and achieve the required gap area by choosing the correct number of lamellas, where the possibly free barely through Flywheel is filled.

The lamellas are pressed in axially from one side and, in addition, especially against twisting secured, which is ensured by a form fit, e.g. with axial grooves and appropriate design of the lamellae or done by a welded or soldered connection can. Particularly in the case of larger quantities, it can be advantageous to place the lamella groups outside of the damper in a device and group by group, e.g. by brazing to connect to the entire set of lamellons then to fix in the damper.

In this version, too, are supported
elastic guide and sealing rings either
with their outside on an inner surface of the
Flange body and with its inside on the
cylindrical or slightly conical part of a
overlapping sheet metal cap, or the bearing rings are attached to an outer diameter of the bearing flange and carry the flywheel directly
without the caps mentioned. In both cases the bearing and seal can either be symmetrical
to the damper center plane or on one side, in which case a second seal / wipe the flange body and the flywheel must be provided. As this seal does not have forces to over

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has to wear, it is increasingly so elastic executed that they have a volume equalization The damper heats up without any significant pressure build-up allows.

In all embodiments, the Task of maintenance-free and wear-free storage or guiding of the flywheel and the sealing of the gap space achieved according to the invention by that at least two elastic bearing and sealing rings with an approximately rectangular cross-section are provided. In order to keep the specific stress and heat development in these rings low keep, they are sized as large as possible and extend over the whole constructively available Broad. It is both possible to make the ring arrangement symmetrically to the center plane so that both rings have bearing and sealing functions, as well as choosing an asymmetrical arrangement, in the case of essentially only one of the rings with a correspondingly wider design, the bearing function takes over, while the other is practically only used for sealing purposes and made of particularly elastic Material is made.

The arrangement of the bearing and sealing rings is still carried out in such a way that the elasticity is not impaired in the circumferential direction the required larger Rigidity for the radial and axial guidance of the swing grain is achieved. That can go through once a slight inclination of the bearing and sealing ring, i.e. due to its limitation by conical surfaces can be achieved. By such a

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Inclination is caused by axial load In addition, a pressure component is effective, which increases the axial rigidity with the sine of the cone angle considerably, while on the other hand the desired rigidity in the radial direction with the cosine of the cone angle only is reduced insignificantly. When not vulcanized Rubber rings, this inclination also has the advantage of being very easy to assemble in the axial direction.

Furthermore - especially with vulcanized rubber rings - there is the possibility of using the round sealing ring on the end face of the fastening flange by means of a disk-shaped extension to extend radially, this part of the bearing ring then between opposite radial surfaces the flange body and the flywheel and is subjected to pressure during axial displacement is, which increases the axial stiffness in a desirable manner.

Finally, the rubber rings themselves can be designed anisotropically in such a way that they behave softly against shear forces in the circumferential direction, but stiffly against those in the axial and radial direction. This can be achieved, for example, by that the ring is made up of layers of different Hardness is built up, with the parting surfaces between softer and harder material always roughly in planes going through the axis lie, or in other words, in the axial

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Plan view of the rubber ring always run approximately radially. Such stiffeners or fins are in place hinder the movement under axial and to a certain extent also under radial stress, while in the case of tangential loading the desired Elasticity in the circumferential direction is practical is not affected. A manufacturing technology favorable design ordered in that the numerous radially extending Stiffeners that are embedded in the bearing and sealing ring are not inserted individually, but are connected in a meandering band, with the kinks are weakened in such a way that there are no significant bending moments with tangential thrust more can occur. Without this weakening, which are usually designed as a predetermined breaking point can, the elasticity would be reduced in an undesirable Veise with tangential stress will.

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In the following, the invention is described using a few exemplary embodiments, which are shown schematically in the drawings. Dahoj z

Fig. 1 shows a conventional learning damper for comparison with internal flywheel;

Fig. 2 shows a lamellar damper with lamellae combined at the fastening edge and over the Bearing rings overlapping sheet metal caps;

Fig. 3 shows a similar damper in which the overarching Sheet metal caps are designed like a membrane on the end face;

4 shows an embodiment in which the damper washers are held together with an overlapping metal cap are, with a sheet metal membrane at the front;

Fig. 5 shows the configuration with similar, in lamellae arranged in an annular space between the flange and the flywheel;

Fig. G shows a similar arrangement in which, however, the elastic bearing and sealing rings are arranged between cone l.mante.1 surfaces;

7 shows a ring between radial surfaces and a asymmetrical damper design;

Fig. 8 shows an embodiment in which the asymmetrical bearing ring on an outer diameter of the Bearing flange is attached, while the other is practically only sealing cams;

9 shows a similar embodiment, but with two symmetrically arranged bearing rings;

Fig. Examples of the anisotropic design of the +11 bearing and sealing rings with a stiffening effect with radial and axial loads.

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In Fife, 1 , for comparison, a convection shock absorber is shown in which the splash grain 1.0 is designed as a housing that completely closes the flywheel 20. Between the two there is d (> r only a few tenths of a millimeter thick and filled with viscous friction agent gap space ^r ) 0, in which the damping work is converted into heat. The annular cover I1 belonging to the flange body 10 closes the housing tightly with a fixed seal 80 or with a weld seam 81. The sliding! agc! 'bushing and the axial bearing ring 91.

In FIG. 2 , the lamp 11 f. The thin sheet metal plates are bent k0 kl pot-shaped at its mounting edge (pairwise different strong) and with its disc-like extension k2. summarized in a flange-like manner towards the inside. The furthest outward lamella 48 also carries the, for example, vulcanized bearing and sealing ring 60, which in this case consists of a conical part and a disk-shaped extension in the axial direction, and which lies on the other side in the overlapping sheet metal cap 30, which in turn is firmly connected to the flywheel 21. In the left half of the figure, another embodiment is shown in which the outer lamella k9 is only present in fragments as a carrier for the bearing and sealing ring 6l. In this example, the flywheel 21 consists of

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several slices and takes near his Outer diameter of the slats-'43 on which together with the lamellas 4θ of the flange body a sufficiently large number of disc-shaped Form gaps 51, of which in this example only 12 are shown. The individual parts of the flywheel 21 are at his outer diameter closed by the ring 22, not only to center these parts, but also to avoid the numerous seals is used between the lamellae, as there are only two fixed seals 80 and 81 close to the Front side required.

Fig. 3 shows a further embodiment of the Laniel 1 endämpf ers, in which the flange body also consists of pairs of differently cranked lamellae kO , 'whose outer on their conical part Λ8 wear the wide bearing and sealing rings 6l. The disk-shaped inner part of the flange body 11, which consists of the combined lamellae and serves to center and fasten the damper to the crankshaft, not shown here, is reinforced here by two ring-shaped disks12. The swing body 21 consists in this embodiment of only one solid ring, which carries two overlapping sheet metal caps 31, which receive the bearing and sealing rings "6.1 on their inner diameter and overlap cylindrically on their outer diameter over the swing body up to its center. This design requires only one seal or weld seam along the damper center plane, due to the elasticity

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the storage and corresponding dimensioning of the caps Jl , these can give way somewhat like a membrane to both sides in the axial direction when internal pressure occurs. In this example, the lamellae 44 of the flywheel are cranked at their fastening edge, whereby the cylindrical extension 45 on the outer diameter serves both to fix the exact distance from the flywheel 21 or from the neighboring lamella as well as for centering and fastening in the cylindrical part of the cap .

In a further embodiment according to FIG. 4 , the wide bearing and sealing rings 62 - here cylindrical - lie with their inner diameter on the correspondingly shaped part 13 of the flange body and directly carry the correspondingly widened outer disk of the flywheel 2J on their outer diameter, which is in its central part numerous discs 24 is composed with spacer rings. These disks 24 form with the lamellae 4O, which are in turn bent at hl and combined at 42, the necessary gap spaces. In this case, for pressure equalization, the annular sheet metal membrane 35 is provided on the end face of the flywheel 21, the inside of which is connected to the gap spaces through the bore 33. The disk-shaped parts 23, 24 and 25 of the flywheel 21 are centered and held together in this embodiment by the overlapping sheet metal cap 34, which enables simple production and sealing.

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Examples of another embodiment are described in FIGS. 5-9 , in which the lamellae are arranged in an annular space between the flange body and the flywheel, the lamellae H6 attached to the flange body by 11 and the lamellae inserted in the flywheel body 21 kh are equal to each other. The topfnrtigon offsets on, jc-.weiligen fastening edge k ^c) and 47 enter the thin lamellae form stability, ensure the correct spacing and serve to secure a good heat transfer. In FIG. 5 , the bearing and sealing ring 6l is held on the flywheel 21 by the sheet metal cap 30, in a manner similar to that described in FIG. On the left-hand side, a similar arrangement with a cylindrical bearing and sealing ring 6Z is shown, which is connected to the flywheel 21 by the cap 31 », which is extended at the end and which is again designed like a membrane. The additional flywheel mass 2ό attached to the flywheel 21 is used to fill an approximately remaining space if the number of lamella pairings kh and ^ 6 required for the application does not fill the available width.

Fig. 6 shows a similar embodiment, in which, however, the flange body 11 consists of the two bearing brackets 13, which are bridged on their outer diameter by the cylindrical ring 1A, which in turn di <; Lamejllen kb Läge. The bearing and sealing rings 6l are arranged here between the conical surface and the flywheel side is again held by the caps 3 ^.

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Fig. 7 shows an asymmetrical design of the flange 11, which has a one-sided attachment 15 as a lamellar and Laperringträger. The second bearing and sealing ring 63 is arranged in this case between radial surfaces of the flange body 11 and the S chvungkö riser 21 and is used here in conjunction with the elastic bearing and sealing ring 6l in particular to absorb axial forces.

Fig. 8 shows ¹ again a non-symmetrical damper design with a simple flange body 11, on the bearing bracket 15 of which the wide sealing and guide ring 62 is placed, which directly carries the one-sided flywheel 21. The gap space 51 formed by the pairs of lamellae hk and 46 is closed off by the overlapping cap 32, which in turn can be made elastic in the manner of a membrane and accommodates the elastic sealing ring 7 ^ on its inner diameter.

Finally, FIG. 9 shows a symmetrically constructed damper in which the T-shaped flange body 11 carries the cylindrical bearing and sealing rings 62 on which the in this case two-part flywheel 21 is mounted.

In the last two FIGS. 10 and Π , the anisotropic design of the bearing and sealing rings is shown, for example. In Fig. 10 , the front view of the ring 64 shows the narrow, radially extending layers of harder material 65, which extend in cross section 60 over the entire surface. The layers of harder material that made up too

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.Rubber types of greater hardness may exist, when thrust forces occur in the Uinfanpsrichtung a little diagonally 66, which with the small angles of inclination of a few degrees that occur here does not affect the elasticity in the direction of the uni. which occurs in the case of a stress indicated by arrows in FIG. 10 in the axial direction and in the radial direction.

In Fig. Π- . an embodiment of the radially extending inserts is shown in which they are connected in a meandering band 67 for manufacturing reasons. So that no stiffening occurs in the circumferential direction 68 during the deformation due to shear forces, the axially extending kinks 69 are weakened and / or designed as breakpoints which break open during operation.

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Claims (22)

Patent claims 1. Torsion damper with internal flange body and external flywheel, which
comprise a plurality of interlocking damper disc whose gaps are filled with a highly viscous fluid and sealed with elastic material, characterized in that the F'anschkörper and / or the Schwüngkörper as Tamp di'ß ferseheiben carry slats which are angled at the fastening edge of cup-like corresponding to the desired distance . 2. Torsional vibration damper according to claim I, characterized in that the thickness of the lamellas is at most five times the width of the gap. 3. Torsional vibration damper according to claim 2, characterized in that the thickness of the lamellas is approximately twice the gap width. 4. Torsional vibration damper according to claim 1, characterized in that the slats are pressed in one piece from sheet metal. 5. torsional vibration damper according to claim 1 characterized g e k e η η ζ e i c h η e. , that the slats are composed of two parts, in particular are welded or soldered. 8098 16/0018 6. Torsional vibration damper according to claim 1, characterized in that the slats are cranked to different degrees and combined at their fastening edges. 7. Torsional vibration damper according to claim 1, characterized in that the lamellae are arranged in an annular space between the flange and the flywheel, the on the paddling body attached slats and the lamellae used in the flywheel are each formed identically. 8. Torsional vibration damper according to claim 1, characterized in that the flywheel is provided with overlapping sheet metal caps, which are on the bearing and sealing rings prop up. 9. Torsional vibration damper according to claim 1, characterized in that the flywheel consists of damper washers, which are held together with an overlapping sheet metal cap are. 10. Torsional vibration damper according to claim 1, characterized in that the overlapping sheet metal caps are dimensioned and designed like a membrane on the front side. 11. Torsional vibration damper according to claim 1, characterized in that at the end a preferably annular sheet metal membrane is attached, the inside of which with the Spa I dream of being connected. 809816/0018 12. Torsional vibration damper according to claim 1, characterized in that between the flange and flywheel at least two elastic bearing and sealing rings with approximately are arranged rectangular cross-section. 13 · torsional vibration damper according to claim 12, d a d \ i r c h g e k e η η ζ e i c h η e t that the rings extend over the entire constructively available width. \H. Torsional vibration damper according to claim 12, characterized in that the rings are arranged between radial surfaces. 15 · Torsional vibration damper according to claim 12, characterized in that the rings are arranged between axial surfaces. 16. Torsional vibration damper according to claim 12, characterized in that the rings are arranged between the surface of the cone are. IT. Torsional vibration damper according to claim 12, d a through marked that the ring arrangement is symmetrical to the center plane and both rings are used for storage and sealing. 18. Torsional vibration damper according to claim 12, as through marked that essentially only one ring absorbs bearing forces, while the other only has sealing functions and made of more elastic material. 8098 16/0018 19. Rotary vibration damper according to Ansnrucli] 2, characterized in that the rings are formed anisotropically in such a way that they oppose thrust forces in the circumferential direction soft, but behave stiffly in the radial and axial direction to absorb the bearing forces. 20. Torsional vibration damper according to claim 19, characterized in that the rings are composed of layers of different hardness, with the separating surfaces in the radial planes containing the central axis lie. 21. Torsional vibration damper according to claim 19, characterized in that the rings are composed of rubber types of different elasticity. 22. Torsional vibration damper according to claim 19, characterized in that Stiffeners are vulcanized into the rings, for example with a meander-shaped sheet metal strip weakened kinks. 809816/0018